CN104884818B - The proportional flow control of fluid pump assemblies - Google Patents
The proportional flow control of fluid pump assemblies Download PDFInfo
- Publication number
- CN104884818B CN104884818B CN201380067489.8A CN201380067489A CN104884818B CN 104884818 B CN104884818 B CN 104884818B CN 201380067489 A CN201380067489 A CN 201380067489A CN 104884818 B CN104884818 B CN 104884818B
- Authority
- CN
- China
- Prior art keywords
- fluid
- valve
- pump
- control assembly
- valve module
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 239000012530 fluid Substances 0.000 title claims abstract description 188
- 230000000712 assembly Effects 0.000 title claims description 15
- 238000000429 assembly Methods 0.000 title claims description 15
- 230000004044 response Effects 0.000 claims abstract description 8
- 238000004891 communication Methods 0.000 claims description 28
- 238000000034 method Methods 0.000 claims description 15
- 238000006073 displacement reaction Methods 0.000 claims description 9
- 230000007246 mechanism Effects 0.000 claims description 8
- 238000012544 monitoring process Methods 0.000 claims description 4
- 241000208340 Araliaceae Species 0.000 claims 1
- 235000005035 Panax pseudoginseng ssp. pseudoginseng Nutrition 0.000 claims 1
- 235000003140 Panax quinquefolius Nutrition 0.000 claims 1
- 235000008434 ginseng Nutrition 0.000 claims 1
- 238000005086 pumping Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 description 2
- 230000008450 motivation Effects 0.000 description 2
- 230000037361 pathway Effects 0.000 description 2
- 230000003213 activating effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 239000002283 diesel fuel Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 239000003502 gasoline Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000007726 management method Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000007935 neutral effect Effects 0.000 description 1
- 238000007634 remodeling Methods 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Classifications
-
- G—PHYSICS
- G05—CONTROLLING; REGULATING
- G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
- G05D7/00—Control of flow
- G05D7/06—Control of flow characterised by the use of electric means
- G05D7/0617—Control of flow characterised by the use of electric means specially adapted for fluid materials
- G05D7/0629—Control of flow characterised by the use of electric means specially adapted for fluid materials characterised by the type of regulator means
- G05D7/0635—Control of flow characterised by the use of electric means specially adapted for fluid materials characterised by the type of regulator means by action on throttling means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
- F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20515—Electric motor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20507—Type of prime mover
- F15B2211/20523—Internal combustion engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
- F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
- F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/63—Electronic controllers
- F15B2211/6303—Electronic controllers using input signals
- F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/65—Methods of control of the load sensing pressure
- F15B2211/651—Methods of control of the load sensing pressure characterised by the way the load pressure is communicated to the load sensing circuit
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/65—Methods of control of the load sensing pressure
- F15B2211/654—Methods of control of the load sensing pressure the load sensing pressure being lower than the load pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/665—Methods of control using electronic components
- F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/865—Prevention of failures
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/0318—Processes
- Y10T137/0324—With control of flow by a condition or characteristic of a fluid
- Y10T137/0368—By speed of fluid
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/8593—Systems
- Y10T137/85978—With pump
- Y10T137/85986—Pumped fluid control
- Y10T137/86027—Electric
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Automation & Control Theory (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A kind of pump control assembly with flow control assembly (16) is disclosed, is arranged between the first end (46) of load sensing valve (42) and fluid pump (20).The flow control assembly may include aperture (112), the first valve module (110), and the second valve module (111).When the first valve module is located at open position and the second valve module is located at first position, the fluid for flowing through the aperture is directed into fluid reservoir and load sensing valve.When the first valve module is located at closed position and the second valve module is located at the second place, the whole fluids for flowing through the aperture are directed into load sensing valve.The operational factor that electronic controller (18) can be configured to the prime mover in response to being powered to fluid pump conveys output current to the first and second valve modules.
Description
The intersection of related application is quoted
The application is submitted on December 20th, 2013 as PCT International Patent Application, and requires on December 21st, 2012
The U.S. Patent Application Serial No.61/740 of submission, 854 priority, it is incorporated herein by reference in full.
Background technology
Fluid system in different application often has different requirements.For example, fluid system may need it is different
Flow rate and different Fluid pressures.Load sensing pump can be used to adjust the operation of pump to meet the different stream of given fluid system
It is dynamic to require.Typical load sensing pump adjusts the flowing requirement of pump using the flowing in fluid system and pressure feedback.Fluid
The variable properties of system for the power source to pump also to proposing different demands.Need the control of improvement pump and the pipe of power source
Reason.
The content of the invention
One aspect of the present invention is related to a kind of pump control assembly.The pump control assembly includes thering is fluid pump and load sensing valve
Fluid pump assemblies.The fluid pump includes fluid intake and fluid issuing.The fluid pump includes variable displacement mechanism.The load sense
Side valve is suitable to adjust the position of variable displacement mechanism.Load sensing valve includes first end and the second end being relatively arranged.Cause
Dynamic device is in fluid communication with fluid pump assemblies.
The pump control assembly also includes the flow control assembly being arranged between the first end of load sensing valve and fluid pump.
In one embodiment, flow control assembly includes aperture, the first valve module and the second valve module.In a configuration, when
When one valve module is located at open position and the second valve module and is located at first position, the part for flowing through the fluid in aperture is directed into
Fluid reservoir, another part for flowing through the fluid in aperture is directed into the first end of load sensing valve.When the first valve module position
When closed position and the second valve module are located at the second place, the of load sensing valve is directed into by whole fluids in aperture
One end.The electronic control unit being electrically connected with the first and second valve modules can also be set.The electronic control unit can match somebody with somebody
The operational factor for being set to the prime mover in response to being powered for fluid pump conveys output current to the first and second valve modules.
Another aspect of the present invention is related to a kind of method for activating pump control assembly.The method may include following step
Suddenly：The pump control assembly is arranged on normal operating condition；Instruction is received to activate what is be associated with the pump control assembly
Actuator；And control valve is transmitted a signal to start actuator.The method may also include one flow control group of commander
To guide, fluid passes through aperture to part from systems pumps and arrival is configured to adjust the load sensing valve that pump flows output.In a step
In, reception system is instructed and reduced with the operational factor based on the prime mover being powered to systems pumps or manage the stream through pump
Body flowing is negative.Another step includes that the first valve of regulation flow control assembly flows through at least of the fluid in aperture with reboot
Assigning to fluid reservoir flow to the fluid of load sensing valve to reduce, while maintaining pump pressure.The method may also include continuously
The step of monitoring prime mover operational factor.
Many additional aspects will in the following description be illustrated.These aspects can relate to the group of single feature and feature
Close.It should be understood that foregoing summary and detailed description below are all exemplary and illustrative, and do not limit public herein
The concept of the broad sense that the implementation method opened is based on.
Brief description of the drawings
Fig. 1 is the schematic diagram of the pump control assembly with exemplary characteristic aspect of principle of the invention.
Fig. 2 is adapted for the schematic diagram of the performance loop used in the pump control assembly of Fig. 1.
Fig. 3 is adapted for the schematic diagram of the fluid pump assemblies used in the pump control assembly of Fig. 1.
Fig. 4 is the diagram of the method for the pump control assembly for service chart 1.
Specific embodiment
Now referring in detail to the illustrative aspect being shown in the drawings of the invention.As possible, make in whole accompanying drawings
Identical or similar structure is presented with like reference characters.
Referring now to Fig. 1, pump control assembly 10 is shown.The pump control assembly 10 is suitable to the position based on actuator to control
The output of fluid pump processed.In the present embodiment, pump control assembly 10 is suitable to be reduced from fluid pump by manipulating load sense wire
Flowing, while maintaining pump output pressure to allow vehicle motor on the peak torque curve under given engine RPM
Operation, and prevent pump load from causing engine stall.Engine stall is for having been converted into being transported on liquified natural gas (LNG)
Capable engine is problem of specific interest, because low side torque output and the engine phase using gasoline or diesel fuel
Than being lowered.Pump control assembly 10 is also suitable for preventing Fluid pressure peak value when actuator reaches its extreme limit of travel.In Fig. 1
In shown embodiment, pump control assembly 10 includes fluid pump assemblies 12, actuator 14, flow control assembly 14 and electronics
Control unit 18.
Fluid pump assemblies
Referring now to Fig. 1 and 3, fluid pump assemblies 12 are described.Fluid pump assemblies 12 include that fluid pump 20 and load sensing are mended
Repay valve module 22.
Fluid pump 20 includes fluid intake 24, fluid issuing 26, discharge port 28 and load sensing ports 30.Fluid pump 20
Fluid intake 24 be in fluid communication with fluid reservoir 32.Fluid issuing 26 is in fluid communication with actuator 16.Discharge port
28 are in fluid communication with fluid reservoir 32.
Fluid pump 20 also includes axle 34.Axle 34 is connected to the power source for rotating axle 34 (for example, engine, motor
Deng).When axle 34 rotates, fluid is pumped into fluid issuing 26 from fluid intake 24.
Fluid pump 20 is variable displacement fluid pump.Used as variable delivery pump, fluid pump 20 includes variable displacement mechanism 36.
In illustrated embodiment, fluid pump 20 is axial poiston pump, and variable displacement mechanism 36 is wobbler.Wobbler 36 can be in
Between/moved between neutrality/neutral gear position and total travel position.In centre position, the discharge capacity of fluid pump 20 is about zero.In zero delivery
Under, when axle 34 rotates, there is no fluid to pass through fluid pump 20.In total travel position, when axle 34 rotates, the maximum amount of fluid leads to
Cross fluid pump 20.
Fluid pump 20 includes control piston 38 and biasing member 40.It is oblique that control piston 38 and biasing member 40 act on rotation
Adjusting the position of wobbler 36 on disk 36.Control piston 38 is suitable to the position of wobbler 36 from total travel position adjustments
To centre position.The selective fluid communication of fluid issuing 26 of control piston 38 and fluid pump 20.Control piston 38 and load
Sensing and compensating valve module 22 is in fluid communication.
Biasing member 40 is suitable to for fluid pump 20 to be biased towards total travel position.Biasing member 40 includes wobbler 36 is inclined
Press to the spring of total travel position.
Load sensing and compensating valve module 22 is suitable to be changed in the flowing of the system using fluid pump 20 and pressure requirements
When change the fluid from fluid pump 20 flow and fluid pressure.In the embodiment shown, sensing and compensating valve module is loaded
22 include load sensing valve 42 and pressure limit compensator 44.In one embodiment, load sensing and compensating valve module 22 is in stream
The outside of body pump 20.In another embodiment, load sensing and compensating valve module 22 is integrated in fluid pump 20.
Load sensing valve 42 provides any one in the discharge port 28 or fluid issuing 26 for control piston 38 and fluid pump 20
Between selectivity fluid communication.In the embodiment shown, load sensing valve 42 is two-bit triplet proportioning valve.In first position
P1, load sensing valve 42 provides the fluid communication between control piston 38 and discharge port 28 so that act on control piston
Fluid on 38 is discharged into fluid reservoir 32 by discharge port 28.When load sensing valve 42 is located at first position P1,
Wobbler 36 is biased component 40 and is biased towards total travel position.
In second place P2, load sensing valve 42 provides the fluid communication between control piston 38 and fluid issuing 26, makes
Pressure fluid is obtained to act on control piston 38.When load sensing valve 42 is located at second place P2, control piston 38 is acted on
So that wobbler 36 is moved towards centre position on biasing member 40.
Load sensing valve 42 includes first end 46 and the second end 48 being oppositely disposed.First end 46 and load sensing ports
30 are in fluid communication.Carry out the fluid matasomatism of self-supported sensing ports 30 in first end 46, load sensing valve 42 is actuated into the
One position.In an illustrated embodiment, light spring 50 is acted also in the first end 46 of load sensing valve 42, and load is felt
Side valve 42 is biased towards first position P1.In one embodiment, the combination acted in the first end 46 of load sensing valve 42 is born
The pressure for being equal to the fluid for carrying out self-supported sensing ports 30 is carried plus about 200psi to about 400psi.
Second end 48 of load sensing valve 42 is in fluid communication with the fluid issuing 26 of fluid pump 20.When acting on the second end 48
On Fluid pressure when being more than the Fluid pressure for acting in first end 46, control piston 38 is caused along towards the direction in centre position
Dynamic wobbler 36, so as to reduce the fluid displacement of first fluid pump 20.
Pressure limit compensator 44 belongs to the type of pressure relief valve.In an illustrated embodiment, pressure limit compensator
44 is two-bit triplet proportioning valve.Pressure limit compensator 44 includes first end 52 and the second end 54 being oppositely disposed.Heavy bullet
Spring 56 is acted in the first end 52 of pressure limit compensator 44, and the fluid matasomatism from fluid issuing 26 is at the second end 54
On.
Pressure limit compensator 44 includes first position PC1 and second place PC2.In first position PC1, pressure limit is mended
Repay device 44 and the fluid passage for leading to discharge port 28 is provided.When pressure limit compensator 44 is located at first position PC1 and load sense
When side valve 42 is located at first position P1, the fluid acted on control piston 38 is discharged into fluid reservoir through discharge port 28
32.In the case where pressure limit compensator 44 is located at first position PC1 and load sensing valve 42 is located at first position P1, rotation
Turn swash plate 36 and be biased part 40 to be biased towards total travel position.
In second place PC2, the fluid that pressure limit compensator 44 is provided between control piston 38 and fluid issuing 26 connects
It is logical, to cause that pressure fluid is acted on control piston 38.The situation of second place PC2 is located in pressure limit compensator 44
Under, control piston 38 is acted on biasing member 40, to cause that wobbler 36 is moved towards centre position.
Rise with the Fluid pressure in fluid issuing 26 and close to the load setting of heavy-duty spring 56, pressure limit is compensated
Device 44 is shifted towards second place PC2, so as to allow fluid to lead to control piston 38.As fluid matasomatism is on control piston 38,
Moved towards centre position the position of wobbler 36.The movement lasts till that the flow at the fluid issuing 26 of fluid pump 20 is sufficiently low
Set or until fluid pump 20 is centrally located with the load that system pressure is maintained heavy-duty spring 56.In a reality
Apply in example, it is for about 2500psi to about 3500psi system pressures that the load that heavy-duty spring 56 is provided is set.
Actuator
Referring now to Fig. 1 and 2, actuator 14 includes actuator 60 and control valve group part 61, and control valve group part 61 has
There are directional control valve 62 and two pilot valves 63a, 63b.Actuator 60 can be linear actuators (such as cylinder etc.) or rotation
Actuator (such as motor etc.).In the present embodiment, actuator 60 is linear actuators.
Actuator 60 includes housing 64.Housing 64 includes the first axial end 65 and the second axial end 66 being oppositely disposed.
Housing 64 limits aperture 67.Piston component 68 is configured in aperture 67.Piston component 68 includes piston 70 and bar 72.
Aperture 67 includes first chamber 74 and second chamber 76.First chamber 74 is configured in the first side of piston 70, and second chamber 76
Configuration is in second side being oppositely disposed of piston 70.
Actuator 60 includes the first control port 82 and the second control port 84.First control port 82 and first chamber 74
It is in fluid communication, and the second control port 84 is in fluid communication with second chamber 76.
Directional control valve 62 is in fluid communication with actuator 60.In an illustrated embodiment, directional control valve 62 is pilot-operated type
Three-position four-way valve.Directional control valve 62 includes first position PD1, and second place PD2 and middle position close centre position PDN.
In first position PD1, directional control valve 62 is provided between the control port 82 of fluid pump 20 and first and the second control
Fluid communication between port processed 84 and fluid reservoir or storage tank 32.In an illustrated embodiment, first position PD1 causes work
Plug assembly 68 stretches out from housing 64.In second place PD2, directional control valve 62 provide the control port 84 of fluid pump 20 and second it
Between and the fluid communication between the first control port 82 and fluid reservoir.In an illustrated embodiment, second place PD2 draws
Play the retraction of piston component 68.
In an illustrated embodiment, directional control valve 62 by pilot valve 63a, 63b activate, pilot valve so by with electronics control
Magnetic valve 86a, 86b actuating of the connection of device processed 18.Multiple centering springs 88 are suitable to for directional control valve 62 to be biased towards centre position
PN1。
Flow-control valve assembly
Referring now to Fig. 1, flow-control valve assembly 16 will be described.Flow-control valve assembly 16 is suitable to controlling pump 20 on demand
Discharge capacity, the torque input needed for this and then control shaft 34.By control for the torque needed for transfer tube 20, the output stream of pump
Amount can be conditioned to be run with the peak value or best torque of engine or other prime mover such as motor, from but regardless of pump 20
Output pressure how can prevent stall.As illustrated, flow-control valve assembly 16 includes the first valve module 110, aperture
112 and second valve module 111.In one embodiment, aperture 112 is configured to provide false pressure drop in the load sense wire,
And can be configured to two gallons per minute by flow rate under cause the pressure drop of about 300psi.The pressure drop in aperture 112 can be with
It is configured to be matched with pump pressure and terminal pressure so that pump reduces flow naturally when increasing by the flow in hole 112.
In an illustrated embodiment, flow-control valve assembly 16 includes entrance 114, outlet 116, load sensing path 118
With vent pathway 120.Entrance 114 is in fluid communication with the fluid issuing 26 of fluid pump 20.Outlet 116 and directional control valve 62 and cause
Pilot valve 63a, 63b of dynamic device assembly 14 are in fluid communication.Load sensing path 118 connects with the fluid of load sensing and compensating valve module 22
It is logical.Vent pathway 120 is in fluid communication with fluid reservoir 32.
First valve module 110 provides the fluid issuing 26 from fluid pump 20 via the valve module of aperture 112 to the second and warp
By port 120 to 32 two flow paths of reservoir.Regardless of the position of the first and second valve modules 110,111, aperture 112
All cause pressure drop in the fluid of pumping of load sensing ports 30 is transported to.In the embodiment shown, the first valve module 110 is
Two-bit triplet proportion magnetic valve.In first position A1, it is blocked from the fluid of the pumping of outlet 26 and cannot pass through the first valve module
110, therefore be forced to flow directly into the second valve module 111 after by aperture 112.In second place A2, the first valve module
110 provide the fluid communication via both the valve module of aperture 112 to the second 111 and reservoir 32 from pump discharge 26, as above institute
State.First valve module 110 is biased towards first position Al by spring 121.
Solenoid 122 activates the first valve module 110 in response to the output current 124 from electronic control unit 18 and (shows
In Fig. 1).Electronic control unit 18 in response to prime mover operational factor such as engine torque demand and/or engine RPM and
Send output current 124.Because the first valve module 110 is proportioning valve, flow and solenoid that fluid passes through the first valve module 110
122 is proportional from the output current 124 of the reception of electronic control unit 18.Therefore, flow direction load sensing ports 30 flow with it is defeated
Go out electric current 124 proportional.
Second valve module 111 is provided between the valve module 110 of fluid issuing 26 and first of fluid pump 20 via aperture 112
Selectivity be in fluid communication.In an illustrated embodiment, the first valve module 110 is 2/2-way magnetic valve.In first position B1,
Second valve module 111 blocks from the fluid of the pumping of outlet 26 and prevents it from directly being connected with load sensing ports 30, but will be negative
Carry sensing ports 30 and be directly discharged to storage tank via port 120, so as to allow pump to be maintained at zero delivery and low standby pressure.
Second place B2, the second valve module 111 is provided from pumping fluid issuing 26 via aperture 112 to the complete of load sensing ports 30
It is complete to be in fluid communication, and block the flowing for leading to discharge port 120.Second valve module 111 is biased towards first position by spring 123
B1。
Solenoid 125 activates the second valve module 111 in response to the output current 127 from electronic control unit 18 and (shows
In Fig. 1).Electronic control unit 18 in response to prime mover operational factor such as engine torque demand and/or engine RPM and
Send output current 127.
Be in fluid communication due to the first end 46 of the load sensing valve 42 of load sensing ports 30 and fluid pump assemblies 12 and
Because load sensing valve 42 is used to adjusting the position of wobbler 36, flow of the position control from fluid pump 20 flows automatically
The flow of body pump 20 is proportional to output current 124.As will be described in more detail, output current 124 can be programmed,
To prevent engine stall and pressure peak.
Operation method
Referring now to Fig. 1-4, the method 1000 of the operation pump control assembly 10 will be described.Although it should be noted that figure
In each step is schematically shown with particular order, but methods described is not necessarily intended to be defined as in the order shown hold
OK.But at least a portion in shown step can in an overlapping manner, different order and/or simultaneously perform.
In step 1002, the system is operated without under normal operating conditions moves actuator 60, wherein logical
It is not powered on and positioned at the position shown in Fig. 1 to the solenoid 122,125 of the first and second valve modules.In this state,
Pump 20 be in it is low standby because load sense signal is discharged into storage tank via port 120.
In step 1004, an instruction is received to start actuator 60, it is therefore desirable to pump fluid.Step 1004 also includes
Start control valve group part 61, wherein signal will be sent to solenoid 86a so that actuator port 84 is in fluid communication with pump 20.
In step 1006, the second control valve group part is commanded to second place B2, therefore pump border collapses, and pump discharge is
Produced to the pumping fluid of load sensing ports 30 by means of the valve module 111 of aperture 112 and second is flowed through.Pushing away over time
Move, pump 20 will improve stroke to flowing full amount, because will for border setting (such as 200-300psi) of load sensing controller
Cannot meet, because being directly connected between pump pressure port 26 and load sensing ports 30, except almost not having by aperture 112
Other limitations.
In step 1008, an instruction is received with the operational factor based on prime mover such as vehicle motor or motor
Reduce or management system flow.If the flow resistance in system causes the pressure of flowing full amount to exceed the torque actuated energy of prime mover
Power, then flow control assembly 16 be activated.During this period, electronic controller 18 is constantly monitored engine torque demand or is only supervised
Survey engine speed (i.e. engine RPM).If after step 1004 and 1006 have begun to, engine RPM drops to low
In setting, this may represent that the engine will stall.
In step 1010, controller to the sending signal of the first valve module 110 so that it is opened in proportion, so as to prevent original
Motivation exceedes the operational factor of prime mover.In other words, the first valve module 110 can be opened to prevent vehicle motor in proportion
Rotating speed is decreased below the threshold engine speed of regulation.In operation, the first valve module 110 continues to open, until by the
One valve module 110 causes the enough pressure drops by aperture 112 to match pump border to the flow of reservoir 32.With the first valve
Component 110 continues to open, and pump border continues to increase, so as to cause pump to reduce discharge capacity and prevent engine stall.When system is at this
When under the pattern of kind, controller 18 will continue to monitor engine RPM, or another parameter, and adjust the first valve module 110 to ensure hair
Motivation will not stall.
It should also be noted that flow-control valve assembly can be configured to slow down actuator prevent impact load.For example, stream
Control valve component can run the pump discharge that cylinder is flowed to be reduced before cylinder just will reach stroke top, with same sample prescription
Formula reduces pump discharge to prevent engine stall.Position sensor can be incorporated into the system to aid in this operation.One
Individual example system includes position sensor, and flow-control valve assembly of the invention can use on April 29th, 2010 to submit to
Entitled fluid pump assemblies control (CONTROL OF A FLUID PUMP ASSEMBLY) U.S. Patent application No.US
12/770,261.US 12/770,261 is incorporated to by reference of text herein.Flow-control valve assembly disclosed by the invention can be used
In substituting valve (ramping valve) component of the valve island of US 12/770,261/tiltedly and be configured to execution and prevent engine stall
And prevent two functions of actuator impact load.
Various remodeling of the invention and modification will be apparent without deviating from the present invention to one skilled in the art
Scope and spirit, and it is to be understood that the scope of the present invention should not be unduly limited to illustrative reality described herein
Example is applied to state.
Claims (10)
1. a kind of pump control assembly, including：
(a) fluid pump assemblies, including：
I. fluid pump, it has fluid issuing and the fluid intake connected with fluid reservoir,
The fluid pump includes variable displacement mechanism；
Ii. load sensing valve, its position for being suitable to adjust variable displacement mechanism, load sensing valve has first end and relatively
The second end for setting；
B () actuator, it is in fluid communication with the fluid pump assemblies；
(c) flow control assembly, it is arranged between the first end of the load sensing valve and the fluid pump, including：
I. aperture, the first valve module and the second valve module；
Characterized in that,
Ii. when second valve module is located at first position, second valve module prevents the fluid issuing pump from fluid pump
The fluid for sending directly is connected with load sensing valve, and load sensing valve is passed directly to fluid reservoir；
Iii. when first valve module is located at open position and second valve module is located at first position, by the hole
Mouthful the part of fluid be directed to fluid reservoir, and another part by the fluid in the aperture is directed to institute
State the first end of load sensing valve；
Iv. when first valve module is located at closed position and second valve module is located at the second place, by the hole
Whole fluids of mouth are directed to the first end of the load sensing valve；
And
The pump control assembly also includes：
(d) electronic control unit, itself and the first valve module and the second valve module electrical communication, wherein, the electronic control unit
The operational factor of the prime mover in response to being powered to fluid pump sends output current to first valve module and the second valve
Component.
2. pump control assembly according to claim 1, wherein, first valve module includes proportion magnetic valve.
3. pump control assembly according to claim 1, wherein, described prime mover is vehicle motor.
4. pump control assembly according to claim 1, wherein, described electronic control unit adjusts first valve module
Position preventing prime mover from dropping below the operational factor.
5. a kind of pump control assembly, including：
(a) fluid pump assemblies, including：
I. fluid pump, it has fluid issuing and the fluid intake connected with fluid reservoir, and the fluid pump includes variable row
Measuring mechanism；
Ii. load sensing valve, its position for being suitable to adjust variable displacement mechanism, load sensing valve has first end and relatively
The second end for setting；
B () actuator, it is in fluid communication with the fluid pump assemblies；
(c) flow control assembly, it is arranged between the first end of the load sensing valve and the fluid pump, including：
I. aperture, the first valve module and the second valve module；
Characterized in that,
Ii. when second valve module is located at first position, second valve module prevents the fluid issuing pump from fluid pump
The fluid for sending directly is connected with load sensing valve, and load sensing valve is passed directly to fluid reservoir；
Iii. when first valve module is located at open position and second valve module is located at first position, by the hole
Mouthful the part of fluid be directed to fluid reservoir, and another part by the fluid in the aperture is directed to institute
State the first end of load sensing valve；
Iv. when first valve module is located at closed position and second valve module is located at the second place, by the hole
Whole fluids of mouth are directed to the first end of the load sensing valve；And
The pump control assembly also includes：
(d) electronic control unit, itself and the first valve module and the second valve module electrical communication, wherein, the electronic control unit
The operational factor of the prime mover in response to being powered to fluid pump sends output current to first valve module and the second valve
Component,
Wherein, described prime mover is vehicle motor, and the operational factor of described prime mover is the minimum speed threshold of the engine
Value.
6. it is a kind of run pump control assembly method, it is characterised in that the described method comprises the following steps：
A pump control assembly is arranged on normal operating condition by ()；
B () receives instruction to activate the actuator being associated with the pump control assembly；
C () transmits a signal to control valve to start actuator；
D () order flow control assembly guides fluid to pass through aperture and lead to from systems pumps to be configured to adjust the negative of pump discharge output
Carry sensing valve；
E the instruction of () reception system is reduced with the operational factor based on prime mover that power is provided to the systems pumps or management is flowed through
The fluid of the pump；And
F () is store by adjusting the first valve of flow control assembly with will be redirected to fluid by least a portion fluid in aperture
Storage and straight by the way that the second valve of flow control assembly to be positioned to prevent fluid stream from systems pumps from sensing valve with load
Passing in succession makes load sensing valve be passed directly to fluid reservoir to reduce the fluid flow that flow direction loads sensing valve, while keeping
The pressure of pump.
7. the method for operation pump control assembly according to claim 6, also including continuously monitoring the fortune of described prime mover
The step of line parameter.
8. the method for operation pump control assembly according to claim 7, wherein, the operation of described continuous monitoring prime mover ginseng
Several steps includes monitoring vehicle engine speed.
9. the method for operation pump control assembly according to claim 8, wherein, adjust the first of the flow control assembly
The step of valve, is including adjusting first valve to prevent engine from falling below the operational factor of prime mover.
10. the method for operation pump control assembly according to claim 9, wherein, adjust the of the flow control assembly
The step of one valve, includes regulation first valve to prevent the engine from falling below minimum speed threshold value.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201261740854P | 2012-12-21 | 2012-12-21 | |
| US61/740,854 | 2012-12-21 | ||
| PCT/US2013/076937 WO2014100594A1 (en) | 2012-12-21 | 2013-12-20 | Proportional flow control of a fluid pump assembly |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104884818A CN104884818A (en) | 2015-09-02 |
| CN104884818B true CN104884818B (en) | 2017-06-30 |
Family
ID=49918929
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380067489.8A Active CN104884818B (en) | 2012-12-21 | 2013-12-20 | The proportional flow control of fluid pump assemblies |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US9323253B2 (en) |
| EP (1) | EP2935904B1 (en) |
| JP (1) | JP6312701B2 (en) |
| CN (1) | CN104884818B (en) |
| WO (1) | WO2014100594A1 (en) |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CA2940679C (en) | 2014-02-28 | 2022-07-19 | Project Phoenix, LLC | Pump integrated with two independently driven prime movers |
| WO2015148662A1 (en) | 2014-03-25 | 2015-10-01 | Afshari Thomas | System to pump fluid and control thereof |
| US10294936B2 (en) | 2014-04-22 | 2019-05-21 | Project Phoenix, Llc. | Fluid delivery system with a shaft having a through-passage |
| WO2015187681A1 (en) | 2014-06-02 | 2015-12-10 | Afshari Thomas | Hydrostatic transmission assembly and system |
| EP3730793B1 (en) | 2014-06-02 | 2022-04-27 | Project Phoenix LLC | Linear actuator assembly and system |
| RU2683005C2 (en) | 2014-07-22 | 2019-03-25 | Проджект Феникс, Ллк | External gear pump integrated with two independently driven prime movers |
| US10072676B2 (en) | 2014-09-23 | 2018-09-11 | Project Phoenix, LLC | System to pump fluid and control thereof |
| US10539134B2 (en) | 2014-10-06 | 2020-01-21 | Project Phoenix, LLC | Linear actuator assembly and system |
| US10677352B2 (en) | 2014-10-20 | 2020-06-09 | Project Phoenix, LLC | Hydrostatic transmission assembly and system |
| EP3344853B1 (en) | 2015-09-02 | 2020-11-04 | Project Phoenix LLC | System to pump fluid and control thereof |
| US11085440B2 (en) | 2015-09-02 | 2021-08-10 | Project Phoenix, LLC | System to pump fluid and control thereof |
| US20180087496A1 (en) * | 2016-09-12 | 2018-03-29 | Flow Control LLC | Automatic self-driving pumps |
| AU2018237126B2 (en) * | 2017-03-22 | 2023-08-03 | Jonathan BALLESTEROS | Low-flow fluid delivery system and low-flow devices therefor |
| US11459220B2 (en) | 2017-11-30 | 2022-10-04 | Danfoss Power Solution II Technology A/S | Hydraulic system with load sense and methods thereof |
| US10801525B2 (en) * | 2018-01-12 | 2020-10-13 | Eaton Intelligent Power Limited | Hydraulic valve with pressure limiter function |
| CN110529449B (en) * | 2019-09-24 | 2021-03-09 | 中国航空工业集团公司沈阳飞机设计研究所 | High-reliability pressure relief device and method for hydraulic servo valve |
| EP4067127B1 (en) * | 2021-03-31 | 2024-06-19 | BeijingWest Industries Co. Ltd. | Suspension hydraulic lift actuator for axle trim height control |
Family Cites Families (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE19517974A1 (en) * | 1995-05-16 | 1996-11-21 | Brueninghaus Hydromatik Gmbh | Slidable hydraulic power or torque control device |
| JP3925666B2 (en) * | 1997-01-20 | 2007-06-06 | 株式会社小松製作所 | Control device for engine and variable displacement pump |
| US6033188A (en) * | 1998-02-27 | 2000-03-07 | Sauer Inc. | Means and method for varying margin pressure as a function of pump displacement in a pump with load sensing control |
| JP3868112B2 (en) * | 1998-05-22 | 2007-01-17 | 株式会社小松製作所 | Control device for hydraulic drive machine |
| DE10219850B3 (en) * | 2002-05-03 | 2004-02-05 | Brueninghaus Hydromatik Gmbh | Control device with limit control valve |
| US7155909B2 (en) * | 2003-05-15 | 2007-01-02 | Kobelco Construction Machinery Co., Ltd. | Hydraulic controller for working machine |
| US6874318B1 (en) * | 2003-09-18 | 2005-04-05 | Sauer-Danfoss, Inc. | Automatic remote pressure compensation in an open circuit pump |
| JP4096901B2 (en) * | 2004-03-17 | 2008-06-04 | コベルコ建機株式会社 | Hydraulic control device for work machine |
| CN101550921A (en) * | 2009-05-05 | 2009-10-07 | 上海电气液压气动有限公司 | Variable control system of plunger variable pump |
| US8607559B2 (en) * | 2009-12-29 | 2013-12-17 | Eaton Corporation | Fluid bypass system |
| US8435010B2 (en) * | 2010-04-29 | 2013-05-07 | Eaton Corporation | Control of a fluid pump assembly |
| MX355682B (en) * | 2010-04-30 | 2018-04-26 | Eaton Corp Star | Multiple fluid pump combination circuit. |
| DE102010052528B4 (en) * | 2010-11-25 | 2021-09-02 | Linde Hydraulics Gmbh & Co. Kg | Load-sensing controlled hydrostatic drive system |
| US9091281B2 (en) | 2011-03-15 | 2015-07-28 | Husco International, Inc. | System for allocating fluid from multiple pumps to a plurality of hydraulic functions on a priority basis |
| CN202165337U (en) * | 2011-06-10 | 2012-03-14 | 韦汉珍 | Hydraulic power system of energy-saving servo variable pump |
| US9347200B2 (en) * | 2012-06-04 | 2016-05-24 | Cnh Industrial America Llc | Fluid control system for work vehicle |
-
2013
- 2013-12-20 CN CN201380067489.8A patent/CN104884818B/en active Active
- 2013-12-20 JP JP2015549781A patent/JP6312701B2/en active Active
- 2013-12-20 WO PCT/US2013/076937 patent/WO2014100594A1/en active Application Filing
- 2013-12-20 EP EP13818164.9A patent/EP2935904B1/en active Active
- 2013-12-20 US US14/136,277 patent/US9323253B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| US20140174549A1 (en) | 2014-06-26 |
| US9323253B2 (en) | 2016-04-26 |
| CN104884818A (en) | 2015-09-02 |
| JP2016506473A (en) | 2016-03-03 |
| WO2014100594A1 (en) | 2014-06-26 |
| EP2935904A1 (en) | 2015-10-28 |
| JP6312701B2 (en) | 2018-04-18 |
| EP2935904B1 (en) | 2019-03-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104884818B (en) | The proportional flow control of fluid pump assemblies | |
| JP4712959B2 (en) | Load detection hydraulic controller for variable displacement pump | |
| CN1989303B (en) | Apparatus and method for controlling work vehicle | |
| EP2652341B1 (en) | Hydraulic system with return pressure control | |
| US9835187B2 (en) | Control system for construction machine | |
| JP5661084B2 (en) | Hydraulic drive device for work machine | |
| US5778669A (en) | Hydraulic positioning system with internal counterbalance | |
| US11105347B2 (en) | Load-dependent hydraulic fluid flow control system | |
| US9080582B2 (en) | Circuit pressure control device, hydraulic control circuit using circuit pressure control unit, and hydraulic control circuit of construction machine | |
| JP2016169818A (en) | Hydraulic driving system | |
| CN107532628A (en) | The oil pressure actuated systems of building machinery | |
| CN105840566B (en) | Hydraulic control device for supplying at least two hydraulic consumers with a pressure medium | |
| CN106321537B (en) | Hydraulic control system and corresponding mobile working device | |
| EP2878816A1 (en) | Pump control device | |
| CN110953197B (en) | Power control hydraulic system and crane | |
| JP2018084196A (en) | Hydraulic drive system | |
| CN103452961B (en) | Open central control unit with constant and regulating pump | |
| EP2956676B1 (en) | Variable load sense open center hybrid system | |
| EP3458727B1 (en) | Electro hydraulic drive and control system | |
| JP2000055003A (en) | Hydrostatic drive device | |
| JP4851857B2 (en) | Method and apparatus for controlling pump flow rate | |
| CN106697044A (en) | Steering hydraulic system and loading machine | |
| EP3470676B1 (en) | Pump device | |
| JP2010048359A (en) | Pump control circuit of construction machine | |
| EP3434910B1 (en) | Shovel and control valve for shovel |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20190621 Address after: Dublin, Ireland Patentee after: Eaton Intelligent Power Co.,Ltd. Address before: Ohio, USA Patentee before: Eaton Corp. |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20220513 Address after: Denmark nordburg Patentee after: Danfoss power system II Technology Co.,Ltd. Address before: Irish Dublin Patentee before: Eaton Intelligent Power Co.,Ltd. |
|
| TR01 | Transfer of patent right | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20231107 Address after: Denmark nordburg Patentee after: DANFOSS A/S Address before: Denmark nordburg Patentee before: Danfoss power system II Technology Co.,Ltd. |